JP2009156422A - Deep groove ball bearing - Google Patents

Deep groove ball bearing Download PDF

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Publication number
JP2009156422A
JP2009156422A JP2007337771A JP2007337771A JP2009156422A JP 2009156422 A JP2009156422 A JP 2009156422A JP 2007337771 A JP2007337771 A JP 2007337771A JP 2007337771 A JP2007337771 A JP 2007337771A JP 2009156422 A JP2009156422 A JP 2009156422A
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Japan
Prior art keywords
deep groove
cage
annular plate
groove ball
annular
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JP2007337771A
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JP5012498B2 (en
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Takeshi Maejima
武始 前島
Yoichi Matsumoto
洋一 松本
Takamichi Tanaka
孝道 田中
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
    • F16C33/785—Bearing shields made of sheet metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a deep groove ball bearing capable of surely feeding lubricating oil to a portion where lubrication insufficiency is liable to occur and prolonging the service life of the bearing even if it rotates at a high speed without using a device that requires an additional space and cost such as a lubricating nozzle or the like. <P>SOLUTION: The deep groove ball bearing includes an inner ring 1, an outer ring 2, a plurality of balls 3 rollingly arranged between the inner and outer rings and a crown-shaped cage 4 formed of resin. The deep groove ball bearing is used in such an environment that the lubricating oil is fed from one side in the axial direction. The annular portion 4a of the crown-shaped cage 4 is directed toward the feeding side of the lubricating oil. An annular plate 5 is disposed on the same side as the annular potion 4a. The annular plate extends inwardly from the inner diameter portion of the crown-shaped cage 4 toward a shoulder 1b of the inner ring 1 in such a state that the annular plate is fixed to the outer ring. An annular opening 10 for feeding the lubricating oil to the inside of the bearing is formed between the inner peripheral portion 5c of the annular plate 5 and the outer peripheral portion of the inner ring 1. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、深溝玉軸受に関し、特に自動車のトランスミッション等の高速回転で使用される深溝玉軸受に関するものである。   The present invention relates to a deep groove ball bearing, and more particularly to a deep groove ball bearing used for high-speed rotation of an automobile transmission or the like.

従来の深溝玉軸受は、図１１に示すように、外周面に内輪軌道溝１０１ａを有する内輪１０１と、内周面に外輪軌道溝１０２ａを有する外輪１０２と、内輪軌道溝１０１ａと外輪軌道溝１０２ａとの間に転動自在に配置された複数の玉１０３と、円環部１０４ａ及び該円環部１０４ａの片方の軸方向端面に突設され、先端に爪部を備えた柱部１０４ｂを有し、該柱部１０４ｂ間に形成された球面ポケット１０４ｃに玉１０３を収容する樹脂製の冠型保持器１０４と、を有する。玉１０３は、冠型保持器１０４によって円周方向に所定の間隔で保持され、保持器１０４と共に公転する。   As shown in FIG. 11, the conventional deep groove ball bearing includes an inner ring 101 having an inner ring raceway groove 101a on the outer peripheral surface, an outer ring 102 having an outer ring raceway groove 102a on the inner peripheral surface, an inner ring raceway groove 101a and an outer ring raceway groove 102a. And a plurality of balls 103 that are arranged so as to be freely rotatable, a ring portion 104a, and a column portion 104b that protrudes from one axial end surface of the ring portion 104a and includes a claw portion at the tip. In addition, the spherical crown 104c formed between the pillar portions 104b includes a resin crown-shaped cage 104 that accommodates the ball 103. The balls 103 are held at predetermined intervals in the circumferential direction by the crown type cage 104 and revolve together with the cage 104.

このような深溝玉軸受は、例えば、自動車の変速機等の回転部に使用される場合、ポンプ等で潤滑油を供給する強制潤滑方式で使用されることが多く、潤滑油は軸受の内部を軸方向に貫通して流れ、変速機ユニット内を潤滑している。   Such deep groove ball bearings are often used in a forced lubrication system in which lubricating oil is supplied by a pump or the like when used in a rotating part of an automobile transmission or the like. It flows through in the axial direction and lubricates the transmission unit.

ところで、この深溝玉軸受を高速回転させると、遠心力により、図１２（ａ）、（ｂ）に示すように、冠型保持器１０４の円環部１０４ａを捩れ軸として、柱部１０４ｂが外径側に開くため、冠型保持器１０４の球面ポケット１０４ｃの内径側と玉１０３との接触面圧が増大し、ポケット１０４ｃの内径側部分１０４ｐが摩耗し、発熱が大きくなるという問題が発生する。   By the way, when the deep groove ball bearing is rotated at a high speed, the column portion 104b is removed by the centrifugal force with the annular portion 104a of the crown-shaped cage 104 as a torsion shaft as shown in FIGS. 12 (a) and 12 (b). Since it opens to the radial side, the contact surface pressure between the inner diameter side of the spherical pocket 104c of the crown-shaped cage 104 and the ball 103 increases, the inner diameter side portion 104p of the pocket 104c wears, and there is a problem that heat generation increases. .

また、ポケット１０４ｃの内径側部分１０４ｐの摩耗が進行すると、冠型保持器１０４の振れ回りが大きくなり、冠型保持器１０４が振動したり、また、図１３に示すように、冠型保持器１０４の外径側と外輪１０２の内周面とが接触して、柱部１０４ｂが摩耗し、最悪の場合は保持器１０４が破損するという問題も発生する。   Further, when the wear of the inner diameter side portion 104p of the pocket 104c progresses, the swing of the crown-shaped cage 104 increases, and the crown-shaped cage 104 vibrates, or, as shown in FIG. The outer diameter side of 104 and the inner peripheral surface of the outer ring 102 come into contact with each other, and the column portion 104b is worn. In the worst case, the cage 104 is damaged.

一方、図１４に示すように、冠型保持器１０４の球面ポケット１０４ｃの中心Ｏを冠型保持器１０４の径方向幅の中心Ｔ１よりも外径側に配置、つまり、冠型保持器１０４の径方向の全幅寸法をＱとした場合に、球面ポケット１０４ｃの中心Ｏより外側の幅Ｑ２よりも内側の幅Ｑ１を大きくして、内径側の玉抱え込み量を大きく確保することで、冠型保持器１０４の外径側への捩れ変形を抑制することが提案されている（例えば、特許文献１参照）。
実開平５−３４３１７号公報 On the other hand, as shown in FIG. 14, the center O of the spherical pocket 104c of the crown-shaped cage 104 is arranged on the outer diameter side from the center T1 of the radial width of the crown-shaped cage 104. When the total width dimension in the radial direction is Q, the inner width Q1 is made larger than the outer width Q2 from the center O of the spherical pocket 104c, and the ball holding amount on the inner diameter side is secured, thereby maintaining the crown shape. It has been proposed to suppress torsional deformation of the container 104 toward the outer diameter side (see, for example, Patent Document 1).
Japanese Utility Model Publication No. 5-34317

しかしながら、図１４に示した特許文献１の深溝玉軸受において、軸受を高速回転させたときには、球面ポケット１０４ｃの内径側が遠心力によって潤滑油不足になることで摩耗し、最終的には捩れ変形を抑えられなくなり、上記した振れ回りによる問題が発生する虞がある。   However, in the deep groove ball bearing of Patent Document 1 shown in FIG. 14, when the bearing is rotated at a high speed, the inner diameter side of the spherical pocket 104 c is worn due to lack of lubricating oil due to centrifugal force, and finally torsional deformation occurs. There is a possibility that the problem due to the above-described swinging may occur.

また、冠型保持器１０４の内周部に潤滑油を供給するため、内輪１０１側に直接潤滑油ノズルを近づけて配置することが考えられるが、潤滑ノズルが別途必要となるため、設置スペースが必要となるなどのデメリットがある。   Further, in order to supply the lubricating oil to the inner peripheral portion of the crown type cage 104, it is conceivable that the lubricating oil nozzle is arranged close to the inner ring 101 side. There are disadvantages such as being necessary.

本発明は、上述した事情に鑑みてなされたものであり、その目的は、潤滑ノズル等の余分なスペースやコストのかかる装置を使用せずに、潤滑不足になりやすい箇所に確実に潤滑油を供給することができ、高速回転時にも軸受寿命の長期化を図ることのできる深溝玉軸受を提供することにある。   The present invention has been made in view of the above-described circumstances, and its purpose is to reliably apply lubricating oil to a place where lubrication is likely to be insufficient without using an extra space such as a lubricating nozzle or an expensive device. It is an object of the present invention to provide a deep groove ball bearing that can be supplied and can extend the life of the bearing even at high speed rotation.

前述した目的を達成するために、本発明に係る深溝玉軸受は、下記（１）〜（１２）を特徴としている。
（１） 外周面に内輪軌道溝を有する内輪と、内周面に外輪軌道溝を有する外輪と、前記外輪軌道溝と前記内輪軌道溝との間に転動自在に配置された複数の玉と、該複数の玉を円周方向に所定の間隔で保持する保持器と、を有し、軸受内部を潤滑するための潤滑油が、前記玉に対して軸方向一方側から供給され、前記玉に対して軸方向他方側から排出される環境下で使用される深溝玉軸受において、
前記軸方向一方側には、前記外輪側に固定された状態で前記内輪の肩部に向けて延びる環状板が設けられており、
該環状板の内周部と前記内輪の外周部との間には、前記軸受内部に前記潤滑油を供給するための環状の開口部が形成されることを特徴とする深溝玉軸受。
（２） 前記保持器は、円環部及び該円環部の片方の軸方向端面に突設された複数の柱部を有し、該柱部間に形成された球面ポケットに前記玉を収容することで該玉を円周方向に所定の間隔で保持する樹脂製の冠型保持器であり、
前記冠型保持器の前記円環部は、前記軸方向一方側に向けて配置されると共に、
前記冠型保持器の径方向幅の中央位置が、前記玉の中心よりも軸受の内径側に偏っていることを特徴とする（１）に記載の深溝玉軸受。
（３） 前記玉の中心が、前記内輪と外輪の軸方向幅の中心位置よりも、前記軸方向他方側にオフセットされていることを特徴とする（１）または（２）に記載の深溝玉軸受。
（４） 前記環状板の内周部と対向する前記内輪の肩部にテーパ状または段差状の切欠きが設けられていることを特徴とする（１）〜（３）のいずれかに記載の深溝玉軸受。
（５） 前記環状板の内周部に、軸受内部側に折り曲げられた折り曲げ壁が設けられていることを特徴とする（１）〜（４）のいずれかに記載の深溝玉軸受。
（６） 前記保持器の球面ポケットの内周部のエッジに面取りまたは曲面が形成されていることを特徴とする（１）〜（５）のいずれかに記載の深溝玉軸受。
（７） 前記環状板の内径が前記玉の公転直径以下に設定されていることを特徴とする（１）〜（６）のいずれか１項に記載の深溝玉軸受。
（８） 前記環状板の内径が前記保持器の内径以下に設定されていることを特徴とする（７）項に記載の深溝玉軸受。
（９） 前記環状の開口部を形成する前記内輪の外周部と前記環状板の内周部との最短距離が前記玉の直径の９％以上であることを特徴とする（１）〜（８）のいずれかに記載の深溝玉軸受。
（１０） 前記環状の開口部を形成する前記内輪の外周部と前記油溜板の内周部との最短距離が前記玉の直径の１１％以上であることを特徴とする（９）に記載の深溝玉軸受。
（１１） 前記環状板が、ハウジングに一体に設けられていることを特徴とする（１）〜（１０）のいずれかに記載の深溝玉軸受。
（１２） 前記外輪の内周部より内径側の前記環状板の外周近傍に、潤滑油の通過を許容する通孔が設けられていることを特徴とする（１）〜（１１）のいずれかに記載の深溝玉軸受。 In order to achieve the above-described object, the deep groove ball bearing according to the present invention is characterized by the following (1) to (12).
(1) An inner ring having an inner ring raceway groove on an outer peripheral surface, an outer ring having an outer ring raceway groove on an inner peripheral surface, and a plurality of balls arranged in a freely rolling manner between the outer ring raceway groove and the inner ring raceway groove; A retainer for holding the plurality of balls in the circumferential direction at a predetermined interval, and lubricating oil for lubricating the inside of the bearing is supplied to the balls from one side in the axial direction, and the balls In deep groove ball bearings used in an environment discharged from the other side in the axial direction,
On the one axial side, an annular plate extending toward the shoulder of the inner ring in a state of being fixed to the outer ring side is provided,
A deep groove ball bearing, wherein an annular opening for supplying the lubricating oil to the inside of the bearing is formed between an inner periphery of the annular plate and an outer periphery of the inner ring.
(2) The cage has an annular part and a plurality of pillars protruding from one axial end face of the annular part, and the ball is accommodated in a spherical pocket formed between the pillars. It is a resin crown-shaped cage that holds the balls in the circumferential direction at a predetermined interval,
The annular portion of the crown-shaped cage is disposed toward one side in the axial direction,
The deep groove ball bearing according to (1), wherein a central position of a radial width of the crown type cage is biased toward an inner diameter side of the bearing with respect to a center of the ball.
(3) The deep groove ball according to (1) or (2), wherein the center of the ball is offset to the other side in the axial direction from the center position of the axial width of the inner ring and the outer ring. bearing.
(4) The tapered portion or stepped notch is provided in the shoulder portion of the inner ring facing the inner peripheral portion of the annular plate, according to any one of (1) to (3), Deep groove ball bearing.
(5) The deep groove ball bearing according to any one of (1) to (4), wherein a bent wall that is bent toward the bearing inner side is provided on an inner peripheral portion of the annular plate.
(6) The deep groove ball bearing according to any one of (1) to (5), wherein a chamfer or a curved surface is formed at an edge of an inner peripheral portion of the spherical pocket of the cage.
(7) The deep groove ball bearing according to any one of (1) to (6), wherein an inner diameter of the annular plate is set to be equal to or less than a revolution diameter of the ball.
(8) The deep groove ball bearing according to (7), wherein an inner diameter of the annular plate is set to be equal to or less than an inner diameter of the cage.
(9) The shortest distance between the outer peripheral portion of the inner ring forming the annular opening and the inner peripheral portion of the annular plate is 9% or more of the diameter of the ball (1) to (8) The deep groove ball bearing according to any one of the above.
(10) The shortest distance between the outer periphery of the inner ring forming the annular opening and the inner periphery of the oil reservoir is 11% or more of the diameter of the ball. Deep groove ball bearing.
(11) The deep groove ball bearing according to any one of (1) to (10), wherein the annular plate is provided integrally with the housing.
(12) Any one of (1) to (11), wherein a through hole that allows passage of lubricating oil is provided in the vicinity of the outer periphery of the annular plate on the inner diameter side of the inner peripheral portion of the outer ring. The deep groove ball bearing described in 1.

上記構成の深溝玉軸受によれば、外輪側に固定された環状板の内周部と内輪の外周部との間の軸方向一方側に、軸受内部に潤滑油を供給するための環状の開口部が形成されているので、その環状の開口部から軸受内部に入り込んだ潤滑油が、保持器の内径側に流入した後に、遠心力によって、玉と保持器の摺動部に流れ込み、さらに遠心力によって流速を増した状態で、開放された内外輪間の軸方向他方側の環状の開口部から軸受外部に排出される。このように、軸受内部に供給された潤滑油が、遠心力によって、保持器の内周側から玉と保持器の摺動部に流れ込むため、潤滑ノズル等の余分なスペースやコストのかかる装置を使用せずに、高速回転時に発生しやすい玉との摺動による保持器の摩耗を抑制することができる。その結果、保持器の振れ回りを防止することができ、軸受の長寿命化を図ることができる。また、遠心力によって流速を増した状態で潤滑油を軸受外部に排出することができるので、潤滑油の入れ替わりを効果的に行うことができ、軸受の温度上昇およびトルク増加を防止することができる。   According to the deep groove ball bearing configured as described above, an annular opening for supplying lubricating oil into the bearing on one axial side between the inner peripheral portion of the annular plate fixed to the outer ring side and the outer peripheral portion of the inner ring. Since the lubricating oil that has entered the inside of the bearing from the annular opening flows into the inner diameter side of the cage, it flows into the sliding portion of the ball and the cage by centrifugal force, and further centrifuges. In a state where the flow rate is increased by force, the air is discharged out of the bearing from the annular opening on the other side in the axial direction between the opened inner and outer rings. Thus, since the lubricating oil supplied to the inside of the bearing flows into the ball and the sliding portion of the cage from the inner peripheral side of the cage by centrifugal force, an extra space and costly device such as a lubrication nozzle is installed. Without using it, it is possible to suppress wear of the cage due to sliding with a ball that is likely to occur during high-speed rotation. As a result, swinging of the cage can be prevented, and the life of the bearing can be extended. Further, since the lubricating oil can be discharged to the outside of the bearing while the flow velocity is increased by centrifugal force, the replacement of the lubricating oil can be performed effectively, and the temperature rise and torque increase of the bearing can be prevented. .

また、樹脂製の冠型保持器は射出成形が可能であるため、大量生産ができ、コストを抑制することができる。なお、冠型保持器は、低トルク化の観点から、玉案内にするのが望ましい。冠型保持器の円環部は、軸方向一方側に向けて配置されているので、この円環部の内周側に沿って潤滑油を玉と保持器の摺動部に流れ込みやすくなる。   Moreover, since the resin-made crown type cage can be injection-molded, it can be mass-produced and the cost can be reduced. The crown type cage is preferably a ball guide from the viewpoint of reducing torque. Since the annular portion of the crown type cage is arranged toward one side in the axial direction, the lubricating oil can easily flow into the sliding portion of the ball and the cage along the inner peripheral side of the annular portion.

また、冠型保持器の径方向幅の中央位置を、玉の中心よりも軸受の内径側に偏らせたので、冠型保持器による玉の抱え込み量を増やすことができ、冠型保持器の捩れ変形を抑制することができる。   In addition, since the central position of the radial width of the crown type cage is biased toward the inner diameter side of the bearing from the center of the ball, the amount of balls held by the crown type cage can be increased. Torsional deformation can be suppressed.

また、玉の中心を軸方向他方側である潤滑油の排出側にオフセットしているので、軸方向一方側である潤滑油の供給側に配置した環状板と玉との間の距離を大きくとることができる。従って、玉と環状板との間隔が開くことにより、潤滑油の供給側を向いた冠型保持器の円環部の軸方向の厚さ、つまり、球面ポケットの底厚を大きくすることができる。その結果、冠型保持器の剛性をアップさせることができ、冠型保持器の振れ回り変形を抑制することができる。   Further, since the center of the ball is offset to the lubricating oil discharge side which is the other side in the axial direction, a distance between the annular plate disposed on the lubricating oil supply side which is the one side in the axial direction and the ball is increased. be able to. Therefore, when the gap between the ball and the annular plate is increased, the axial thickness of the annular portion of the crown-shaped cage facing the supply side of the lubricant, that is, the bottom thickness of the spherical pocket can be increased. . As a result, the rigidity of the crown type cage can be increased, and the deformation of the crown type cage can be suppressed.

また、環状板が配設された側の内輪の肩部に、テーパ状または段差状の切欠きが設けられているので、潤滑油の流入する環状の開口部を大きめに確保しつつ、環状板の内径をより小さくすることができる。その結果、保持器の内径側に潤滑油を確実に導入することができ、球面ポケットと玉との摺動部へ潤滑油を導きやすくなる。   In addition, since a tapered or stepped notch is provided in the shoulder portion of the inner ring on the side where the annular plate is disposed, the annular plate is secured while ensuring a large annular opening into which lubricating oil flows. The inner diameter of can be made smaller. As a result, the lubricating oil can be reliably introduced to the inner diameter side of the cage, and the lubricating oil can be easily guided to the sliding portion between the spherical pocket and the ball.

また、環状板の内周部に軸受内部側に延びる折り曲げ壁があるので、環状板の内周部と内輪の外周部との間に確保された環状の開口部から流入する潤滑油を、遠心力に負けずに、保持器の内周部の方向に積極的に導くことができる。   Also, since there is a bent wall extending to the bearing inner side at the inner peripheral part of the annular plate, the lubricating oil flowing from the annular opening secured between the inner peripheral part of the annular plate and the outer peripheral part of the inner ring is centrifuged. Without losing force, it can be actively guided toward the inner periphery of the cage.

また、保持器の球面ポケットの内周部のエッジに面取りまたは曲面が形成されるので、エッジが玉に接触した場合にも、保持器側の応力集中を緩和することができ、保持器の摩耗を減らすことができる。特に、保持器の内径が小さくなった場合、エッジがシャープになるが、そのエッジに面取りまたは曲面を形成することにより、摩耗の軽減を図ることができる。   In addition, since the chamfered or curved surface is formed at the inner peripheral edge of the spherical pocket of the cage, the stress concentration on the cage side can be reduced even when the edge contacts the ball, and the wear of the cage is reduced. Can be reduced. In particular, when the inner diameter of the cage is reduced, the edge becomes sharp, but wear can be reduced by forming a chamfer or a curved surface at the edge.

また、環状板の内径を玉の公転直径以下、より好ましくは、保持器の内径以下としているので、環状板により潤滑油を必要箇所に送り込む性能を向上させることができ、軸受の潤滑状態をよくすることができる。   Also, since the inner diameter of the annular plate is less than or equal to the revolution diameter of the ball, and more preferably less than the inner diameter of the cage, the performance of feeding the lubricating oil to the required location by the annular plate can be improved, and the bearing is well lubricated. can do.

また、内輪の外周部と環状板の内周部との最短距離を玉の直径の９％以上としているので、保持器の振れ回り低減を図ることができる。   In addition, since the shortest distance between the outer peripheral portion of the inner ring and the inner peripheral portion of the annular plate is 9% or more of the diameter of the ball, it is possible to reduce the whirling of the cage.

また、内輪の外周部と環状板の内周部との最短距離を玉の直径の１１％以上としているので、より確実に保持器の振れ回りを低減することができる。   Further, since the shortest distance between the outer peripheral portion of the inner ring and the inner peripheral portion of the annular plate is 11% or more of the diameter of the ball, it is possible to reduce the whirling of the cage more reliably.

また、環状板をハウジングと一体に設けたので、部品点数を削減することができる。   Further, since the annular plate is provided integrally with the housing, the number of parts can be reduced.

また、環状板の外周近傍に設けた通孔を設けることで、この通孔を通して、潤滑油が自由に逃げることができるので、軸受内部外周側の潤滑油の交換効率が上がり、発熱防止を図ることができる。   Further, by providing a through hole provided in the vicinity of the outer periphery of the annular plate, the lubricating oil can freely escape through the through hole, so that the efficiency of replacing the lubricating oil on the inner peripheral side of the bearing is increased, and heat generation is prevented. be able to.

以下、本発明の深溝玉軸受に係る好適な実施形態を図面に基づいて詳細に説明する。   Hereinafter, preferred embodiments of the deep groove ball bearing of the present invention will be described in detail with reference to the drawings.

＜第１実施形態＞ <First Embodiment>

図１に示すように、この深溝玉軸受は、外周面に内輪軌道溝１ａを有する内輪１と、内周面に外輪軌道溝２ａを有する外輪２と、内輪軌道溝１ａと外輪軌道溝２ａとの間に転動自在に配置された複数の玉（鋼球）３と、玉３を円周方向に所定の間隔で保持する樹脂製の冠型保持器４と、内輪１と外輪２の軸方向の一方の端面側に設けられた薄板よりなる環状板５と、を備えている。   As shown in FIG. 1, this deep groove ball bearing includes an inner ring 1 having an inner ring raceway groove 1a on the outer peripheral surface, an outer ring 2 having an outer ring raceway groove 2a on the inner peripheral surface, an inner ring raceway groove 1a and an outer ring raceway groove 2a. A plurality of balls (steel balls) 3 that are arranged so as to roll freely between them, a resin crown-shaped cage 4 that holds the balls 3 in the circumferential direction at predetermined intervals, and the shafts of the inner ring 1 and the outer ring 2 And an annular plate 5 made of a thin plate provided on one end face side in the direction.

冠型保持器４は、図２に示すように、円環部４ａと、該円環部４ａの片方の軸方向端面に突設されて一定間隔で並ぶ複数の柱部４ｂと、隣接する柱部４ｂ間に確保された球面状内側面を有する球面ポケット４ｃと、を備えるものであり、玉３を各球面ポケット４ｃに収容することで、玉３を円周方向に所定の間隔で保持している。   As shown in FIG. 2, the crown-shaped cage 4 includes an annular portion 4a, a plurality of pillar portions 4b that protrude from one axial end face of the annular portion 4a and are arranged at a constant interval, and adjacent pillars. Spherical pockets 4c having spherical inner surfaces secured between the portions 4b, and by holding the balls 3 in the respective spherical pockets 4c, the balls 3 are held at predetermined intervals in the circumferential direction. ing.

冠型保持器４を構成する樹脂の例としては、４６ナイロンや６６ナイロンなどのポリアミド系樹脂、ポリブチレンテレフタレート、ポリフェレンサルサイド（ＰＰＳ）、ポリアミドイミド（ＰＡＩ）、熱可塑性ポリイミド、ポリエーテルエーテルケトン（ＰＥＥＫ）、ポリエーテルニトリル（ＰＥＮ）などが挙げられる。また、上記した樹脂に１０〜５０ｗｔ％の繊維状充填材（例えば、ガラス繊維や炭素繊維など）を適宜添加することにより、冠型保持器４の剛性および寸法精度を向上させることができる。   Examples of the resin constituting the crown cage 4 include polyamide resins such as 46 nylon and 66 nylon, polybutylene terephthalate, polyferlen salside (PPS), polyamide imide (PAI), thermoplastic polyimide, polyether ether ketone. (PEEK), polyether nitrile (PEN) and the like. Moreover, the rigidity and dimensional accuracy of the crown type cage 4 can be improved by appropriately adding 10 to 50 wt% of a fibrous filler (for example, glass fiber or carbon fiber) to the above-described resin.

また、この冠型保持器４は、好ましくは多点ゲートの射出成形で製作する。そうすれば、冠型保持器４の寸法精度を、１点ゲートのものに比べて向上させることができる。また、多点ゲートで製作することで、ウェルド部を保持器の最弱部位であるポケット底からずらすことができるので、ウェルド部による強度低下を防止できる。   The crown type cage 4 is preferably manufactured by injection molding of a multipoint gate. Then, the dimensional accuracy of the crown type cage 4 can be improved as compared with the one-point gate. In addition, since the weld portion can be displaced from the pocket bottom, which is the weakest part of the cage, by manufacturing with a multipoint gate, it is possible to prevent a decrease in strength due to the weld portion.

この深溝玉軸受は、軸受内部を潤滑するための潤滑油が、玉３に対して軸方向一方側Ａから供給され、玉３に対して軸方向他方側Ｂから排出されるような環境下で使用される。そして、冠型保持器４は、円環部４ａを軸方向一方側である潤滑油の供給側Ａに向けるように配置されており、供給された潤滑油を円環部４ａの内周面に沿って、玉３と保持器４の摺動部に導くことができる。   In this deep groove ball bearing, the lubricating oil for lubricating the inside of the bearing is supplied from the one axial side A to the ball 3 and discharged from the other axial side B to the ball 3. used. The crown-shaped cage 4 is arranged so that the annular portion 4a faces the lubricating oil supply side A which is one side in the axial direction, and the supplied lubricating oil is disposed on the inner peripheral surface of the annular portion 4a. Along the ball 3 and the sliding portion of the cage 4.

また、外輪２の潤滑油の供給側Ａには、環状板５が加締め固定されている。環状板５は、外輪２の外輪軌道溝２ａの側方の肩部に形成された係合溝２ｂに外周端５ａを係合させることにより外輪２に固定されており、環状板部５ｂを内輪１の内輪軌道溝１ａの側方の肩部１ｂに向けて延ばしている。そして、環状板５の内周部５ｃと内輪１の肩部１ｂの外周部との間に、潤滑油が供給される環状の開口部１０が形成される。   An annular plate 5 is caulked and fixed to the lubricating oil supply side A of the outer ring 2. The annular plate 5 is fixed to the outer ring 2 by engaging an outer peripheral end 5a with an engagement groove 2b formed on a side shoulder portion of the outer ring raceway groove 2a of the outer ring 2, and the annular plate portion 5b is fixed to the inner ring. The inner ring raceway groove 1a extends toward the side shoulder 1b. An annular opening 10 to which lubricating oil is supplied is formed between the inner peripheral portion 5 c of the annular plate 5 and the outer peripheral portion of the shoulder portion 1 b of the inner ring 1.

この場合、環状板５の内周部５ｃと対向する内輪１の肩部１ｂにはテーパ状の切欠き１ｃが設けられており、テーパ状の切欠き１ｃの外周面と環状板５の内周部５ｃとの間に、潤滑油の供給される環状の開口部１０が形成される。このテーパ状の切欠き１ｃは、潤滑油の流入性向上のために、冠型保持器４の球面ポケットの底よりも軸方向内側まで延びている。   In this case, the shoulder 1b of the inner ring 1 facing the inner peripheral portion 5c of the annular plate 5 is provided with a tapered notch 1c, and the outer peripheral surface of the tapered notch 1c and the inner periphery of the annular plate 5 are provided. An annular opening 10 to which lubricating oil is supplied is formed between the portion 5c. The tapered notch 1c extends to the inner side in the axial direction from the bottom of the spherical pocket of the crown type retainer 4 in order to improve the inflow of lubricating oil.

また、図３（ａ）に示すように、冠型保持器４の径方向幅の中央位置４ｈは、玉３の抱きかかえ量を増やすため、玉３の中心Ｏよりも軸受の内径側に偏っている。このように、保持器４の径方向幅の中心が玉３の中心と一致する場合（図３（ｂ）参照）と比較して、冠型保持器４を内径側に偏在させて、玉３の抱きかかえ量を大きくすると、冠型保持器４が遠心力によって外側に広がるときに、保持器４の内周部のエッジ４ｅと玉３との径方向隙間ｅ２を、図３（ｂ）の隙間ｅ１より小さくできる。従って、外径側への保持器４の変形を小さく抑えることができ、その結果、図３（ｂ）のように抱え込み量が小さい場合よりも、捩れ変形を抑制でき、保持器４の外輪２との接触を防止できる。   Further, as shown in FIG. 3A, the central position 4h of the radial width of the crown-shaped cage 4 is more biased toward the inner diameter side of the bearing than the center O of the ball 3 in order to increase the holding amount of the ball 3. ing. Thus, compared with the case where the center of the radial width of the cage 4 coincides with the center of the ball 3 (see FIG. 3B), the crown-shaped cage 4 is unevenly distributed on the inner diameter side, and the ball 3 When the holding amount is increased, the radial gap e2 between the edge 4e of the inner peripheral portion of the retainer 4 and the ball 3 when the crown retainer 4 spreads outward by centrifugal force is shown in FIG. 3 (b). It can be made smaller than the gap e1. Accordingly, the deformation of the cage 4 toward the outer diameter side can be suppressed to a small value. As a result, the torsional deformation can be suppressed as compared with the case where the amount of holding is small as shown in FIG. Can be prevented.

また、内輪１の外径面と保持器４の内周部との距離が小さくなることにより、内輪１の外径面が保持器４の回転のガイド作用をなし、保持器４の半径方向のガタを抑制して、保持器４の振れ回りを防止する効果を期待できる。なお、通常回転時には、保持器４は玉案内され、保持器４と内輪１は接触しないため、軸受トルクが増加することがない。また、保持器４に衝撃力などの突発的な力が加わった場合には、保持器４と内輪１が接触する可能性があるが、その場合でも、保持器４が外輪２と接触する場合に比べて、軸受トルクの増加が少なくてすむ。なお、特に衝撃力が作用する条件下で使用される場合には、保持器４の案内を玉案内から内輪案内に変更してもかまわない。   Further, since the distance between the outer diameter surface of the inner ring 1 and the inner peripheral portion of the cage 4 becomes smaller, the outer diameter surface of the inner ring 1 serves as a guide for rotation of the cage 4, and the radial direction of the cage 4 The effect of suppressing the play and preventing the cage 4 from swinging can be expected. During normal rotation, the cage 4 is guided by the ball, and the cage 4 and the inner ring 1 do not contact with each other, so that the bearing torque does not increase. Further, when a sudden force such as an impact force is applied to the cage 4, the cage 4 and the inner ring 1 may come into contact with each other, but even in that case, the cage 4 comes into contact with the outer ring 2. Compared with, the increase in bearing torque is small. Note that the guide of the cage 4 may be changed from the ball guide to the inner ring guide, particularly when used under conditions where an impact force acts.

さらに、図４（ａ）に示すように、球面ポケット４ｃの内周部のエッジ４ｅには曲面が付けられている。上記したように、保持器４の内径が小さくなると、図４（ａ）の仮想線のように、球面ポケット４ｃの内周部のエッジ４ｅが鋭角的になり、この部分が摩耗しやすくなる。そこで、本実施形態のように、断面曲面状のエッジ４ｅとすることで、摩耗を防止することができる。なお、図４（ｂ）や図４（ｃ）に示すように、エッジ４ｅには、面取りが施されてもよく、また、これらの場合、玉３が保持器４に接触しやすい球面ポケット４ｃの底や爪先端にのみ、部分的に曲面や面取りを設けてもよい。また、図４（ｃ）に示す円筒形状の面取りの場合には、図４（ａ）や図４（ｂ）に示すような曲面や面取りに比べ、射出成形用の金型の製作が容易であり、コストが抑えられるためより好ましい。   Further, as shown in FIG. 4A, a curved surface is attached to the edge 4e of the inner peripheral portion of the spherical pocket 4c. As described above, when the inner diameter of the cage 4 is reduced, the edge 4e of the inner peripheral portion of the spherical pocket 4c becomes acute as shown by the phantom line in FIG. 4A, and this portion is easily worn. Therefore, wear can be prevented by using the edge 4e having a curved cross section as in this embodiment. As shown in FIGS. 4B and 4C, the edge 4e may be chamfered. In these cases, the spherical pocket 4c in which the ball 3 is easy to contact the cage 4 is used. A curved surface or chamfer may be partially provided only on the bottom or the tip of the nail. In addition, in the case of the cylindrical chamfer shown in FIG. 4 (c), it is easier to manufacture a mold for injection molding than the curved surface or chamfer as shown in FIG. 4 (a) or 4 (b). It is more preferable because the cost can be suppressed.

また、図１に示すように、本実施形態の深溝玉軸受では、玉３の中心Ｏが、内輪１と外輪２の軸方向幅の中心位置Ｌよりも、潤滑油の排出側Ｂに適当な寸法Ｆだけオフセットされている。このように玉３の位置を潤滑油の排出側Ｂにオフセットした場合、潤滑油の供給側Ａに配設した環状板５と玉３の間の軸方向距離が開く。従って、その分だけ、冠型保持器４の球面ポケット４ｃの底厚Ｊ（円環部４ａの肉厚）を大きく確保することができる。このように、保持器４の球面ポケット４ｃの底厚Ｊを増やすと、それだけ冠型保持器４の剛性アップを図ることができ、遠心力による捩れ変形を抑制する効果が高まる。   Further, as shown in FIG. 1, in the deep groove ball bearing of the present embodiment, the center O of the ball 3 is more suitable for the lubricating oil discharge side B than the center position L of the axial width of the inner ring 1 and the outer ring 2. Offset by dimension F. Thus, when the position of the ball 3 is offset to the lubricating oil discharge side B, the axial distance between the annular plate 5 disposed on the lubricating oil supply side A and the ball 3 is increased. Accordingly, the bottom thickness J of the spherical pocket 4c of the crown type cage 4 (the thickness of the annular portion 4a) can be ensured by a corresponding amount. Thus, if the bottom thickness J of the spherical pocket 4c of the retainer 4 is increased, the rigidity of the crown retainer 4 can be increased accordingly, and the effect of suppressing torsional deformation due to centrifugal force is enhanced.

また、本実施形態の深溝玉軸受では、環状板５の内周部に、軸受内部側に折り曲げられた折り曲げ壁５ｄが設けられている。このように軸受内部側に延びる折り曲げ壁５ｄを設けると、環状の開口部１０から流入した潤滑油が、遠心力により直ぐに外径側に向かわずに、折り曲げ壁５ｄに誘導されて、冠型保持器４の内周部に向かうようになり、潤滑の必要な部位に積極的に潤滑油を流れ込ませることができる。   Further, in the deep groove ball bearing of the present embodiment, a bent wall 5 d that is bent toward the bearing inner side is provided on the inner peripheral portion of the annular plate 5. When the bending wall 5d extending in the bearing inner side is provided in this way, the lubricating oil flowing in from the annular opening 10 is guided to the bending wall 5d without being directed to the outer diameter side due to the centrifugal force, and retained in the crown shape. It comes to go to the inner peripheral part of the container 4, and lubricating oil can be actively poured into the site | part which needs lubrication.

また、環状板５の内周部５ｃの内径Ｄｓは、玉３の公転直径ＰＣＤ以下、より好ましくは、冠型保持器４の内径Ｄｈ以下としている。   Further, the inner diameter Ds of the inner peripheral portion 5 c of the annular plate 5 is not more than the revolution diameter PCD of the ball 3, more preferably not more than the inner diameter Dh of the crown type cage 4.

また、環状の開口部１０を形成している内輪１の外周部と環状板５の内周部５ｃとの最短距離ｙは、玉３の直径Ｄｗの９％以上、より好ましくは１１％以上に設定されている。この場合、最短距離ｙは、環状板５の内径をＤｓ、内輪１の肩部１ｂの外径をＤ１とした場合、
ｙ＝（Ｄｓ−Ｄ１）／２
となる。 The shortest distance y between the outer peripheral portion of the inner ring 1 forming the annular opening 10 and the inner peripheral portion 5c of the annular plate 5 is 9% or more, more preferably 11% or more of the diameter Dw of the ball 3. Is set. In this case, the shortest distance y is set so that the inner diameter of the annular plate 5 is Ds and the outer diameter of the shoulder 1b of the inner ring 1 is D1.
y = (Ds−D1) / 2
It becomes.

本実施形態の深溝玉軸受によれば、外輪２に固定された環状板５の内周部５ｃと内輪１の外周部との間の軸方向供給側に、環状の開口部１０が形成されているので、その環状の開口部１０から軸受内部に潤滑油を導入することができる。そして、軸受内部に入り込んだ潤滑油は、冠型保持器４の内径側に流入した後に、遠心力によって、玉３と保持器４の摺動部に流れ込み、さらに遠心力によって流速を増した状態で、開放された内外輪１、２間の軸方向排出側の環状の開口部から軸受外部に排出される。なお、図１中の矢印は潤滑油の流れを示している。   According to the deep groove ball bearing of the present embodiment, the annular opening 10 is formed on the axial supply side between the inner periphery 5 c of the annular plate 5 fixed to the outer ring 2 and the outer periphery of the inner ring 1. Therefore, the lubricating oil can be introduced into the bearing through the annular opening 10. Then, after the lubricating oil that has entered the inside of the bearing flows into the inner diameter side of the crown type cage 4, it flows into the sliding portion of the ball 3 and the cage 4 by centrifugal force, and further increases the flow velocity by the centrifugal force. Then, it is discharged to the outside of the bearing from the annular opening on the axial discharge side between the opened inner and outer rings 1 and 2. In addition, the arrow in FIG. 1 has shown the flow of lubricating oil.

このように、軸受内部に供給された潤滑油が、遠心力によって、冠型保持器４の内径側から玉３と保持器４の摺動部に流れ込むため、潤滑ノズル等の余分なスペースやコストのかかる装置を使用せずに、高速回転時に発生しやすい玉３との摺動による保持器４の摩耗を抑制することができる。その結果、冠型保持器４の振れ回りを防止することができ、軸受の長寿命化を図ることができる。また、遠心力によって流速を増した状態で潤滑油を軸受外部に排出することができるので、潤滑油の入れ替わりを効果的に行うことができ、軸受の温度上昇およびトルク増加を防止することができる。   Thus, since the lubricating oil supplied to the inside of the bearing flows into the sliding portion of the ball 3 and the cage 4 from the inner diameter side of the crown type cage 4 by centrifugal force, extra space and cost such as a lubrication nozzle Without using such a device, it is possible to suppress wear of the cage 4 due to sliding with the balls 3 that are likely to occur during high-speed rotation. As a result, it is possible to prevent the crown-type cage 4 from swinging and to prolong the life of the bearing. Further, since the lubricating oil can be discharged to the outside of the bearing while the flow velocity is increased by centrifugal force, the replacement of the lubricating oil can be performed effectively, and the temperature rise and torque increase of the bearing can be prevented. .

また、樹脂製の冠型保持器４は射出成形が可能であるため、大量生産ができ、コストを抑制しながら、潤滑状態の改善を図ることができる。また、玉案内である冠型保持器４は、低トルク化に寄与することができる。   Moreover, since the resin-made crown type cage 4 can be injection-molded, it can be mass-produced, and the lubrication state can be improved while the cost is suppressed. Moreover, the crown type cage 4 which is a ball guide can contribute to a reduction in torque.

また、環状板５の内径Ｄｓを、冠型保持器４の内径Ｄｈ以下とすることで、環状の開口部１０から軸受内部に入り込んだ潤滑油が、冠型保持器４の内径側により確実に流入することができる。   In addition, by setting the inner diameter Ds of the annular plate 5 to be equal to or less than the inner diameter Dh of the crown-shaped cage 4, the lubricating oil that has entered the bearing from the annular opening 10 is more reliably disposed on the inner diameter side of the crown-shaped cage 4. Can flow in.

また、本実施形態の深溝玉軸受によれば、冠型保持器４の径方向幅の中央位置４ｈを、玉３の中心Ｏよりも軸受の内径側に偏らせているので、冠型保持器４による玉３の抱え込み量を増やすことができ、冠型保持器４の捩れ変形を抑制することができる。   Further, according to the deep groove ball bearing of the present embodiment, the center position 4h of the radial width of the crown-shaped cage 4 is biased toward the inner diameter side of the bearing with respect to the center O of the ball 3, so that the crown-shaped cage 4 can increase the holding amount of the balls 3, and the torsional deformation of the crown type cage 4 can be suppressed.

また、玉３の中心Ｏを潤滑油の排出側Ｂにオフセットしているので、潤滑油の供給側Ａに配置した環状板５と玉３との間の距離を大きくとることができ、玉３と環状板５との間隔が開くことにより、潤滑油の供給側Ａを向いた冠型保持器４の円環部４ａの軸方向の厚さ、つまり、球面ポケット４ｃの底厚Ｊを大きくすることができる。その結果、冠型保持器４の剛性をアップさせることができ、冠型保持器４の振れ回り変形を抑制することができる。   In addition, since the center O of the ball 3 is offset to the lubricating oil discharge side B, the distance between the annular plate 5 and the ball 3 arranged on the lubricating oil supply side A can be increased. And the annular plate 5 are widened to increase the axial thickness of the annular portion 4a of the crown-shaped retainer 4 facing the lubricating oil supply side A, that is, the bottom thickness J of the spherical pocket 4c. be able to. As a result, the rigidity of the crown-shaped cage 4 can be increased, and the swinging deformation of the crown-shaped cage 4 can be suppressed.

また、環状板５が配設された側の内輪１の肩部１ｂに、テーパ状の切欠き１ｃを設けているので、潤滑油の流入する環状の開口部１０を大きめに確保しつつ、環状板５の内径Ｄｓを小さくすることができる。その結果、冠型保持器４の内径側に潤滑油を確実に導入することができ、球面ポケット４ｃと玉３との摺動部へ潤滑油を導きやすくなる。   Further, since the tapered notch 1c is provided in the shoulder portion 1b of the inner ring 1 on the side where the annular plate 5 is disposed, the annular opening 10 into which the lubricating oil flows is secured while being large. The inner diameter Ds of the plate 5 can be reduced. As a result, the lubricating oil can be reliably introduced into the inner diameter side of the crown type cage 4, and the lubricating oil can be easily guided to the sliding portion between the spherical pocket 4 c and the ball 3.

また、環状板５の内周部５ｃに軸受内部側に延びる折り曲げ壁５ｄを設けているので、環状板５の内周部５ｃと内輪１の外周部との間に確保された環状の開口部１０から流入する潤滑油を、遠心力に負けずに、冠型保持器４の内周部の方向に積極的に導くことができる。   Further, since the inner peripheral portion 5c of the annular plate 5 is provided with a bent wall 5d extending toward the bearing inner side, an annular opening portion secured between the inner peripheral portion 5c of the annular plate 5 and the outer peripheral portion of the inner ring 1 is provided. The lubricating oil flowing in from 10 can be actively guided toward the inner peripheral portion of the crown-shaped cage 4 without losing centrifugal force.

また、冠型保持器４の球面ポケット４ｃの内周部のエッジ４ｅに面取りまたは曲面が形成されるので、エッジ４ｅが玉３に接触した場合にも、保持器４側の応力集中を緩和することができ、保持器４の摩耗を減らすことができる。特に、冠型保持器４の内径が小さくなった場合、エッジ４ｅがシャープになるが、そのエッジ４ｅに面取りまたは曲面を形成することにより、摩耗の軽減を図ることができる。   In addition, since chamfering or a curved surface is formed on the edge 4e of the inner peripheral portion of the spherical pocket 4c of the crown-shaped cage 4, even when the edge 4e contacts the ball 3, stress concentration on the cage 4 side is alleviated. Thus, the wear of the cage 4 can be reduced. In particular, when the inner diameter of the crown-shaped cage 4 becomes small, the edge 4e becomes sharp. However, wear can be reduced by forming a chamfer or a curved surface on the edge 4e.

また、環状板５の内径Ｄｓを玉３の公転直径ＰＣＤ以下、より好ましくは、冠型保持器の内径以下としているので、環状板５により潤滑油を必要箇所に送り込む性能を向上させることができ、軸受の潤滑状態をよくすることができる。特に、内輪１の外周部と環状板５の内周部５ｃとの最短距離ｙを玉３の直径Ｄｗの９％以上とした場合は、冠型保持器４の振れ回り低減を図ることができるし、内輪１の外周部と環状板５の内周部５ｃとの最短距離ｙを玉３の直径Ｄｗの１１％以上とした場合は、より確実に冠型保持器４の振れ回りを低減することができる。   Further, since the inner diameter Ds of the annular plate 5 is set to be equal to or less than the revolution diameter PCD of the ball 3, more preferably less than the inner diameter of the crown-type cage, the performance of feeding the lubricating oil to the necessary place by the annular plate 5 can be improved. The lubrication state of the bearing can be improved. In particular, when the shortest distance y between the outer peripheral portion of the inner ring 1 and the inner peripheral portion 5c of the annular plate 5 is set to 9% or more of the diameter Dw of the ball 3, it is possible to reduce the whirling of the crown type cage 4. When the shortest distance y between the outer peripheral portion of the inner ring 1 and the inner peripheral portion 5c of the annular plate 5 is 11% or more of the diameter Dw of the ball 3, the swinging of the crown type cage 4 is more reliably reduced. be able to.

＜第２実施形態＞
図５は第２実施形態の深溝玉軸受の要部断面図である。
この深溝玉軸受では、外輪２の内周部より内径側の環状板５の外周近傍に、潤滑油の通過を許容する通孔５ｅが設けられている。このように構成することで、環状板５の外周近傍に設けた通孔５ｅを通して潤滑油が自由に逃げることができるので、軸受内部外周側の軸受内部の領域Ｇにおいて、潤滑油の交換効率を上げることができ、その部分の発熱防止を図ることができる。その他の構成及び効果は、第１実施形態のものと同様である。 Second Embodiment
FIG. 5 is a cross-sectional view of the main part of the deep groove ball bearing of the second embodiment.
In this deep groove ball bearing, a through hole 5 e that allows passage of lubricating oil is provided in the vicinity of the outer periphery of the annular plate 5 on the inner diameter side from the inner peripheral portion of the outer ring 2. With this configuration, the lubricating oil can freely escape through the through hole 5e provided in the vicinity of the outer periphery of the annular plate 5, so that the lubricating oil replacement efficiency can be improved in the region G inside the bearing on the outer peripheral side of the bearing. It is possible to prevent heat generation at that portion. Other configurations and effects are the same as those of the first embodiment.

なお、本発明は、上述した実施形態に限定されるものではなく、適宜、変形、改良等が可能である。その他、上述した実施形態における各構成要素の材質、形状、寸法、数、配置箇所等は本発明を達成できるものであれば任意であり、限定されない。   In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

図６（ａ）〜（ｅ）は、本発明の深溝玉軸受の第１〜第５変形例を示す概略構成図である。なお、これらの構成は、以下に説明する部分を除いて、上記実施形態と同様の構成及び効果を有する。   FIGS. 6A to 6E are schematic configuration diagrams showing first to fifth modifications of the deep groove ball bearing of the present invention. These configurations have the same configurations and effects as those of the above-described embodiment except for portions described below.

図６（ａ）の第１変形例に係る深溝玉軸受は、内輪１の肩部１ｂに、テーパ状の切欠き１ｃの代わりに、段差状の切欠き１ｄを設けている。   The deep groove ball bearing according to the first modification of FIG. 6A is provided with a stepped notch 1d in the shoulder 1b of the inner ring 1 instead of the tapered notch 1c.

図６（ｂ）の第２変形例に係る深溝玉軸受は、内輪１の肩部１ｂに、テーパ状の切欠き１ｃの代わりに、段差状の切欠き１ｄを設け、折り曲げ壁５ｄを、冠型保持器４の円環部４ａの内周側に入る位置まで延ばしたものである。   In the deep groove ball bearing according to the second modified example of FIG. 6B, a stepped notch 1d is provided on the shoulder 1b of the inner ring 1 in place of the tapered notch 1c, and the bent wall 5d is provided with a crown. It extends to a position that enters the inner peripheral side of the annular portion 4 a of the mold cage 4.

図６（ｃ）の第３変形例に係る深溝玉軸受は、内輪１の肩部１ｂに、テーパ状の切欠き１ｃの代わりに、段差状の切欠き１ｄを設け、環状体５の内周部５ｃに折り曲げ壁５ｄがない構成である。この場合は、折り曲げ壁５ｄがないので、環状の開口部１０から流入した潤滑油が、遠心力によって外径方向に行きがちであるが、環状の開口部１０から軸受内部に流入する時点で、潤滑油には運動エネルギーが付与されているので、十分に冠型保持器４の内周部に潤滑油を導くことができる。   The deep groove ball bearing according to the third modification of FIG. 6C is provided with a stepped notch 1d instead of the tapered notch 1c on the shoulder 1b of the inner ring 1, The configuration is such that the portion 5c does not have the bent wall 5d. In this case, since there is no bending wall 5d, the lubricating oil flowing in from the annular opening 10 tends to go in the outer diameter direction due to centrifugal force, but when it flows into the bearing from the annular opening 10, Since the kinetic energy is given to the lubricating oil, the lubricating oil can be sufficiently guided to the inner peripheral portion of the crown type cage 4.

図６（ｄ）の第４変形例に係る深溝玉軸受は、内輪１の肩部１ｂに切欠きが無い構成であり、冠型保持器４の内周部と内輪１の外径面が接近する。また、環状体５の内周部５ｃに折り曲げ壁５ｄがない構成である。   The deep groove ball bearing according to the fourth modified example of FIG. 6D has a configuration in which the shoulder 1b of the inner ring 1 is not cut away, and the inner peripheral portion of the crown-type cage 4 and the outer diameter surface of the inner ring 1 are close to each other. To do. In addition, the inner peripheral portion 5c of the annular body 5 has no bent wall 5d.

図６（ｅ）の第５変形例に係る深溝玉軸受は、内輪１の肩部１ｂに切欠き１ｄが無い構成である。また、冠型保持器４は、保持器４の径方向幅の中心が玉３の中心と一致するものが使用され、冠型保持器４の内周部と内輪１の外径面との接触を抑制している。また、この保持器４を使用することで、環状板５の内径は、保持器４の内径より小さくなり、保持器４の内周側と内輪１との間に潤滑油が通りやすくなる。   The deep groove ball bearing according to the fifth modification of FIG. 6 (e) has a configuration in which the shoulder 1 b of the inner ring 1 has no notch 1 d. The crown type cage 4 is used in which the center of the radial width of the cage 4 coincides with the center of the ball 3, and the inner peripheral portion of the crown type cage 4 and the outer diameter surface of the inner ring 1 are in contact with each other. Is suppressed. Further, by using this cage 4, the inner diameter of the annular plate 5 becomes smaller than the inner diameter of the cage 4, and the lubricating oil can easily pass between the inner peripheral side of the cage 4 and the inner ring 1.

さらに、図７（ａ）〜（ｄ）は、本発明の深溝玉軸受の第６〜第９変形例を示す概略構成図である。例えば、上述した実施形態では、外輪２の肩部に直接、環状板５が取り付けられているが、図７（ａ）、（ｂ）に示す第６及び第７変形例のように、外輪２の外側面に側板３５、４５を配設して、その側板３５に設けた環状凸部３５ａや側板４５そのものを環状板として用いてもよい。また、図７（ｃ）、（ｄ）に示す第８及び第９変形例のように、外輪２を固定するハウジング５０、６０に内向きフランジ部５５、６５を設け、そのフランジ部５５に設けた環状凸部３５ａやフランジ部６５そのものを環状板として用いてもよい。   Further, FIGS. 7A to 7D are schematic configuration diagrams showing sixth to ninth modifications of the deep groove ball bearing of the present invention. For example, in the above-described embodiment, the annular plate 5 is directly attached to the shoulder portion of the outer ring 2. However, as in the sixth and seventh modifications shown in FIGS. Alternatively, the side plates 35 and 45 may be disposed on the outer surface of each of the two plates, and the annular protrusion 35a provided on the side plate 35 or the side plate 45 itself may be used as the annular plate. Further, as in the eighth and ninth modifications shown in FIGS. 7C and 7D, inward flange portions 55 and 65 are provided in the housings 50 and 60 for fixing the outer ring 2, and the flange portions 55 are provided. The annular convex portion 35a or the flange portion 65 itself may be used as the annular plate.

このように構成することで、部品点数を削減することができ、また、環状板の外周端を外輪の係合溝に加締める工程も省略でき、コストが削減できる。また、これら第６〜第９変形例では、外輪２に環状板が固定される構成と比べて、内輪１と外輪２との間の軸方向一方側にスペースを設けやすく、保持器４の円環部４ａを厚くすることができる。   With this configuration, the number of parts can be reduced, and the step of crimping the outer peripheral end of the annular plate into the engagement groove of the outer ring can be omitted, thereby reducing the cost. Further, in these sixth to ninth modifications, it is easier to provide a space on one side in the axial direction between the inner ring 1 and the outer ring 2 than the configuration in which the annular plate is fixed to the outer ring 2, and the circle of the cage 4 The ring portion 4a can be thickened.

さらに、上記実施形態では、環状板として、内輪１の肩部１ｂの外周面と非接触な遮蔽板が使用されているが、接触シールを使用する場合には、環状板の内周部側に供給孔が設けられてもよい。   Furthermore, in the said embodiment, although the shielding board which is non-contact with the outer peripheral surface of the shoulder part 1b of the inner ring | wheel 1 is used as an annular plate, when using a contact seal, the inner peripheral part side of an annular plate is used. Supply holes may be provided.

また、使用される保持器としては、波型プレス保持器や２つの部材を係合してなる組み合わせ型の保持器など、他の保持器にも適用できる。   Moreover, as a holder used, it is applicable also to other holders, such as a corrugated press holder and a combination type holder formed by engaging two members.

次に、図８に示す深溝玉軸受を用いて、保持器半径方向ガタ測定試験の例について述べる。なお、この深溝玉軸受は、図６（ｃ）に示す第３変形例に係るものと略同様の構成であり、試験１では、内輪１の肩部１ｂの端部外径Ｄ１を変化させ、試験２では、環状板１５の内径Ｄｓを変化させている。   Next, an example of a cage radial play test will be described using the deep groove ball bearing shown in FIG. The deep groove ball bearing has substantially the same configuration as that according to the third modification shown in FIG. 6C. In Test 1, the outer diameter D1 of the end portion 1b of the inner ring 1 is changed, In Test 2, the inner diameter Ds of the annular plate 15 is changed.

＜試験１＞
本試験１では、環状板１５の内径Ｄｓを５１．８ｍｍに固定し、内輪１の肩部１ｂの端部外径Ｄ１を変化させることにより、ｙ／Ｄｗ（隙間／玉径）を変化させ、摩耗量の指針として、新品と比べた保持器半径方向ガタ増加量を調査した。なお、軸受構成及び試験条件は、以下の通りである。 <Test 1>
In the test 1, the inner diameter Ds of the annular plate 15 is fixed to 51.8 mm, and the end outer diameter D1 of the shoulder 1b of the inner ring 1 is changed to change y / Dw (gap / ball diameter), As a guide for the amount of wear, the amount of increase in the radial play of the cage compared to the new one was investigated. The bearing configuration and test conditions are as follows.

＜軸受構成＞
・ 軸受形式：６９０９（ＰＣＤ＝５６．５ｍｍ）
・ 玉径：６．７ｍｍ
・ 保持器：球面ポケットを有する冠型保持器
・ 保持器材料：ガラス繊維２５％強化４６ナイロン
・ 保持器円環部と環状板の環状板部間の距離Ｄｂ：１ｍｍ
・ 保持器内径Ｄｈ：５１．８ｍｍ
＜試験条件＞
・回転数：３００００ｒｐｍ
・給油温度：１２０℃
・潤滑方法ＶＧ２４の鉱油を強制潤滑給油（０．１Ｌ／ｍｉｎ）
・荷重：２５００Ｎ
・試験時間：２０Ｈｒ <Bearing configuration>
・ Bearing type: 6909 (PCD = 56.5mm)
・ Ball diameter: 6.7mm
-Cage: Crown type cage with spherical pockets-Cage material: Glass fiber 25% reinforced 46 nylon-Distance Db: 1mm between cage annular part and annular plate part of annular plate
・ Cage inner diameter Dh: 51.8 mm
<Test conditions>
・ Rotation speed: 30000 rpm
・ Oil supply temperature: 120 ℃
・ Lubrication method VG24 mineral oil forced lubrication (0.1 L / min)
・ Load: 2500N
・ Test time: 20 hours

結果は、表１及び図９の通りであった。   The results were as shown in Table 1 and FIG.

Figure 2009156422
Figure 2009156422

図９に示した摩耗試験結果により、ｙ／Ｄｗが９％以上となると、深溝玉軸受の振れ回り開始時間の向上がほぼ飽和し、ｙ／Ｄｗが１１％以上となると、振れ回り開始時間の向上が完全に飽和することが分かる。これより、ｙ／Ｄｗは９％以上、好ましくは１１％以上であると、振れ回り低減に対して大きな効果が得られることが検証された。また、ｙ／Ｄｗが３％以下だと、環状の開口部１０が狭すぎて、潤滑油が十分に供給できずに軸受が焼きついた。   According to the result of the wear test shown in FIG. 9, when y / Dw is 9% or more, the improvement of the swing start time of the deep groove ball bearing is almost saturated, and when y / Dw is 11% or more, the swing start time It can be seen that the improvement is completely saturated. From this, it was verified that if y / Dw is 9% or more, preferably 11% or more, a great effect can be obtained for reduction of runout. On the other hand, when y / Dw was 3% or less, the annular opening 10 was too narrow, and the lubricating oil could not be sufficiently supplied, and the bearing was burned.

＜試験２＞
本試験２では、図８に示すような深溝玉軸受において、内輪１の外径Ｄ１を４８．４ｍｍに固定し、環状板１５の内径Ｄｓを変化させ、摩耗量の指針として、新品と比べた保持器半径方向ガタ増加量を調査した。但し、ｙ／Ｄｗは、常に試験１において飽和領域となる１１％以上に設定している。なお、軸受構成及び試験条件は試験１と同様である。 <Test 2>
In this test 2, in the deep groove ball bearing as shown in FIG. 8, the outer diameter D1 of the inner ring 1 is fixed to 48.4 mm, and the inner diameter Ds of the annular plate 15 is changed. The increase in the radial play of the cage was investigated. However, y / Dw is always set to 11% or more, which is the saturation region in Test 1. The bearing configuration and test conditions are the same as in Test 1.

結果は、表２及び図１０の通りであった。   The results were as shown in Table 2 and FIG.

Figure 2009156422
Figure 2009156422

図１０に示した摩耗試験結果により、環状板の内径を軸受ＰＣＤ以下にし始めた辺りから摩耗量が減少していることが分かる。これは保持器４の間に潤滑油が流入し難くなり、潤滑油の多くが保持器４の内径に流れ始めるからであると考えることができる。この効果は、環状板１５の内径Ｄｓを保持器４の内径Ｄｈ以下にするとほぼ飽和している。これらのことより、環状板１５の内径Ｄｓは、軸受ＰＣＤ以下、好ましくは保持器４の内径Ｄｈ以下にすべきであることが分かる。   From the results of the wear test shown in FIG. 10, it can be seen that the amount of wear has decreased from the point where the inner diameter of the annular plate has begun to become less than or equal to the bearing PCD. It can be considered that this is because the lubricating oil hardly flows between the cages 4 and much of the lubricating oil starts to flow into the inner diameter of the cage 4. This effect is almost saturated when the inner diameter Ds of the annular plate 15 is less than or equal to the inner diameter Dh of the cage 4. From these facts, it can be seen that the inner diameter Ds of the annular plate 15 should be not more than the bearing PCD, preferably not more than the inner diameter Dh of the cage 4.

本発明の第１実施形態の深溝玉軸受の要部断面図である。It is principal part sectional drawing of the deep groove ball bearing of 1st Embodiment of this invention. 冠型保持器の構成例を示す斜視図である。It is a perspective view which shows the structural example of a crown type holder | retainer. （ａ）は、本実施形態の冠型保持器の径方向幅の中心位置が玉の中心より内径側に偏っている場合、（ｂ）は冠型保持器の径方向幅の中心位置が玉の中心に一致する場合をそれぞれ示す図である。(A) is when the center position of the radial width of the crown type cage of the present embodiment is biased to the inner diameter side from the center of the ball, (b) is the center position of the radial width of the crown type cage is the ball FIG. 前記冠型保持器の球面ポケットの内周部のエッジの処理の仕方を示す図で、（ａ）はエッジに曲面を付けた場合を示す図、（ｂ）はエッジに面取りを施した場合を示す図、（ｃ）はエッジに他の面取りを施した場合を示す図である。It is a figure which shows the method of processing the edge of the inner peripheral part of the spherical pocket of the said crown type retainer, (a) is a figure which shows the case where a curved surface is given to an edge, (b) is the case where chamfering is given to an edge. The figure shown, (c) is a figure which shows the case where other chamfering is given to the edge. 本発明の第２実施形態の深溝玉軸受の要部断面図である。It is principal part sectional drawing of the deep groove ball bearing of 2nd Embodiment of this invention. （ａ）〜（ｅ）は、本発明の第１〜第５変形例に係る深溝玉軸受を示す要部概略断面図である。(A)-(e) is a principal part schematic sectional drawing which shows the deep groove ball bearing which concerns on the 1st-5th modification of this invention. （ａ）〜（ｄ）は、本発明の第６〜第９変形例に係る深溝玉軸受を示す要部概略断面図である。(A)-(d) is a principal part schematic sectional drawing which shows the deep groove ball bearing which concerns on the 6th-9th modification of this invention. 本発明の試験１及び試験２に使用される深溝玉軸受の概略断面図である。It is a schematic sectional drawing of the deep groove ball bearing used for Test 1 and Test 2 of the present invention. 本発明の第２実施形態の軸受における数値限定の意義を検証する第１の試験結果を示すグラフである。It is a graph which shows the 1st test result which verifies the significance of the numerical limitation in the bearing of 2nd Embodiment of this invention. 同軸受の第２の試験結果を示すグラフである。It is a graph which shows the 2nd test result of the bearing. 従来の冠型保持器を有した深溝玉軸受の要部断面図である。It is principal part sectional drawing of the deep groove ball bearing which has the conventional crown type cage. （ａ）及び（ｂ）は冠型保持器の問題点の説明のために示す円周方向断面図及び軸方向断面図である。(A) And (b) is the circumferential direction sectional view and axial direction sectional view shown for description of the problem of a crown type cage. 冠型保持器が摩耗した場合の問題点を説明するための図である。It is a figure for demonstrating a problem when a crown type holder | retainer wears. （ａ）は従来の冠型保持器の例を示す断面図、（ｂ）は外周から見た部分側面図である。(A) is sectional drawing which shows the example of the conventional crown type holder | retainer, (b) is the partial side view seen from the outer periphery.

符号の説明Explanation of symbols

１ 内輪
１ａ 内輪軌道溝
１ｂ 肩部
１ｃ テーパ状の切欠き
１ｄ 段差状の切欠き
２ 外輪
２ａ 外輪軌道溝
３ 玉
４ 冠型保持器
４ａ 円環部
４ｂ 柱部
４ｃ ポケット
４ｅ エッジ
４ｈ 冠型保持器の径方向幅の中心位置
５，３５，４５，５５，６５ 環状板
５ｃ 内周部
５ｄ 折り曲げ壁
１０ 環状の開口部
Ｏ 玉の中心
Ｌ 内輪と外輪の軸方向幅の中心
Ｄ１ 内輪の外径
Ｄｓ 環状板の内径
Ｄｈ 冠型保持器の内径
ＰＣＤ 玉の公転直径 DESCRIPTION OF SYMBOLS 1 Inner ring 1a Inner ring raceway groove 1b Shoulder part 1c Tapered notch 1d Stepped notch 2 Outer ring 2a Outer ring raceway groove 3 Ball 4 Crown type retainer 4a Ring part 4b Column part 4c Pocket 4e Edge 4h Crown type retainer 5, 45, 55, 65 Annular plate 5 c Inner peripheral part 5 d Bending wall 10 Annular opening O Center of ball L Center of axial width of inner ring and outer ring D 1 Outer diameter of inner ring Ds Inner diameter of annular plate Dh Inner diameter of crown type cage PCD Revolving diameter of ball

Claims (12)

外周面に内輪軌道溝を有する内輪と、内周面に外輪軌道溝を有する外輪と、前記外輪軌道溝と前記内輪軌道溝との間に転動自在に配置された複数の玉と、該複数の玉を円周方向に所定の間隔で保持する保持器と、を有し、軸受内部を潤滑するための潤滑油が、前記玉に対して軸方向一方側から供給され、前記玉に対して軸方向他方側から排出される環境下で使用される深溝玉軸受において、
前記軸方向一方側には、前記外輪側に固定された状態で前記内輪の肩部に向けて延びる環状板が設けられており、
該環状板の内周部と前記内輪の外周部との間には、前記軸受内部に前記潤滑油を供給するための環状の開口部が形成されることを特徴とする深溝玉軸受。 An inner ring having an inner ring raceway groove on an outer peripheral surface, an outer ring having an outer ring raceway groove on an inner peripheral surface, a plurality of balls arranged in a freely rollable manner between the outer ring raceway groove and the inner ring raceway groove, And a retainer for holding the ball at a predetermined interval in the circumferential direction, and lubricating oil for lubricating the inside of the bearing is supplied from one axial direction to the ball, In deep groove ball bearings used in an environment discharged from the other side in the axial direction,
On the one axial side, an annular plate extending toward the shoulder of the inner ring in a state of being fixed to the outer ring side is provided,
A deep groove ball bearing, wherein an annular opening for supplying the lubricating oil to the inside of the bearing is formed between an inner periphery of the annular plate and an outer periphery of the inner ring. 前記保持器は、円環部及び該円環部の片方の軸方向端面に突設された複数の柱部を有し、該柱部間に形成された球面ポケットに前記玉を収容することで該玉を円周方向に所定の間隔で保持する樹脂製の冠型保持器であり、
前記冠型保持器の前記円環部は、前記軸方向一方側に向けて配置されると共に、
前記冠型保持器の径方向幅の中央位置が、前記玉の中心よりも軸受の内径側に偏っていることを特徴とする請求項１に記載の深溝玉軸受。 The retainer has an annular portion and a plurality of pillar portions projecting from one axial end face of the annular portion, and the ball is accommodated in a spherical pocket formed between the pillar portions. A crown-shaped cage made of resin that holds the balls at predetermined intervals in the circumferential direction;
The annular portion of the crown-shaped cage is disposed toward the one side in the axial direction,
The deep groove ball bearing according to claim 1, wherein a central position of a radial width of the crown type cage is biased toward an inner diameter side of the bearing with respect to a center of the ball. 前記玉の中心が、前記内輪と外輪の軸方向幅の中心位置よりも、前記軸方向他方側にオフセットされていることを特徴とする請求項１または２に記載の深溝玉軸受。   3. The deep groove ball bearing according to claim 1, wherein the center of the ball is offset to the other side in the axial direction from the center position of the axial width of the inner ring and the outer ring. 前記環状板の内周部と対向する前記内輪の肩部にテーパ状または段差状の切欠きが設けられていることを特徴とする請求項１〜３のいずれか１項に記載の深溝玉軸受。   The deep groove ball bearing according to any one of claims 1 to 3, wherein a tapered or stepped notch is provided in a shoulder portion of the inner ring facing the inner peripheral portion of the annular plate. . 前記環状板の内周部に、軸受内部側に折り曲げられた折り曲げ壁が設けられていることを特徴とする請求項１〜４のいずれか１項に記載の深溝玉軸受。   The deep groove ball bearing according to any one of claims 1 to 4, wherein a bent wall that is bent toward an inner side of the bearing is provided on an inner peripheral portion of the annular plate. 前記保持器の球面ポケットの内周部のエッジに面取りまたは曲面が形成されていることを特徴とする請求項１〜５のいずれか１項に記載の深溝玉軸受。   The deep groove ball bearing according to any one of claims 1 to 5, wherein a chamfer or a curved surface is formed at an edge of an inner peripheral portion of the spherical pocket of the cage. 前記環状板の内径が前記玉の公転直径以下に設定されていることを特徴とする請求項１〜６のいずれか１項に記載の深溝玉軸受。   The deep groove ball bearing according to claim 1, wherein an inner diameter of the annular plate is set to be equal to or less than a revolution diameter of the ball. 前記環状板の内径が前記保持器の内径以下に設定されていることを特徴とする請求項７に記載の深溝玉軸受。   The deep groove ball bearing according to claim 7, wherein an inner diameter of the annular plate is set to be equal to or smaller than an inner diameter of the cage. 前記環状の開口部を形成する前記内輪の外周部と前記環状板の内周部との最短距離が前記玉の直径の９％以上であることを特徴とする請求項１〜８のいずれか１項に記載の深溝玉軸受。   The shortest distance between the outer peripheral part of the inner ring and the inner peripheral part of the annular plate forming the annular opening is 9% or more of the diameter of the ball. The deep groove ball bearing described in the item. 前記環状の開口部を形成する前記内輪の外周部と前記油溜板の内周部との最短距離が前記玉の直径の１１％以上であることを特徴とする請求項９に記載の深溝玉軸受。   The deep groove ball according to claim 9, wherein the shortest distance between the outer peripheral portion of the inner ring forming the annular opening and the inner peripheral portion of the oil reservoir plate is 11% or more of the diameter of the ball. bearing. 前記環状板が、ハウジングに一体に設けられていることを特徴とする請求項１〜１０のいずれか１項に記載の深溝玉軸受。   The deep groove ball bearing according to claim 1, wherein the annular plate is provided integrally with the housing. 前記外輪の内周部より内径側の前記環状板の外周近傍に、潤滑油の通過を許容する通孔が設けられていることを特徴とする請求項１〜１１のいずれか１項に記載の深溝玉軸受。   The through-hole which accept | permits passage of lubricating oil is provided in the outer periphery vicinity of the said annular plate of the inner peripheral side of the said outer ring | wheel from the inner peripheral part. Deep groove ball bearing.
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JP2011133046A (en) * 2009-12-25 2011-07-07 Nsk Ltd Rolling bearing
JP2011256914A (en) * 2010-06-08 2011-12-22 Nsk Ltd Deep groove ball bearing
JP2014077508A (en) * 2012-10-11 2014-05-01 Ntn Corp Angular ball bearing and cage used in the same
CN108869550A (en) * 2018-08-10 2018-11-23 镇江鑫可轴承有限公司 A kind of combined retainer type roller bearing
CN109798298A (en) * 2019-03-26 2019-05-24 洛阳新强联回转支承股份有限公司 A kind of oversize high-speed centrifugal casting machine bearing
US20220389968A1 (en) * 2021-06-07 2022-12-08 Aktiebolaget Skf Rolling bearing
US11781595B2 (en) 2021-06-07 2023-10-10 Aktiebolaget Skf Deep groove ball bearing
USRE49737E1 (en) * 2008-12-10 2023-11-28 Nsk Ltd. Ball bearing
FR3137730A1 (en) * 2022-07-06 2024-01-12 Skf Bearing for motor or electric machine
CN109798298B (en) * 2019-03-26 2024-06-07 洛阳新强联回转支承股份有限公司 Bearing of oversized high-speed centrifugal casting machine

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Cited By (11)

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USRE49737E1 (en) * 2008-12-10 2023-11-28 Nsk Ltd. Ball bearing
JP2011133046A (en) * 2009-12-25 2011-07-07 Nsk Ltd Rolling bearing
JP2011256914A (en) * 2010-06-08 2011-12-22 Nsk Ltd Deep groove ball bearing
JP2014077508A (en) * 2012-10-11 2014-05-01 Ntn Corp Angular ball bearing and cage used in the same
CN108869550A (en) * 2018-08-10 2018-11-23 镇江鑫可轴承有限公司 A kind of combined retainer type roller bearing
CN108869550B (en) * 2018-08-10 2023-09-26 镇江鑫可轴承有限公司 Combined retainer type roller bearing
CN109798298A (en) * 2019-03-26 2019-05-24 洛阳新强联回转支承股份有限公司 A kind of oversize high-speed centrifugal casting machine bearing
CN109798298B (en) * 2019-03-26 2024-06-07 洛阳新强联回转支承股份有限公司 Bearing of oversized high-speed centrifugal casting machine
US20220389968A1 (en) * 2021-06-07 2022-12-08 Aktiebolaget Skf Rolling bearing
US11781595B2 (en) 2021-06-07 2023-10-10 Aktiebolaget Skf Deep groove ball bearing
FR3137730A1 (en) * 2022-07-06 2024-01-12 Skf Bearing for motor or electric machine

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